Automatic web rewinding machine



J. KlEVlT 2,650,038

AUTOMATIC WEB REWINDING MACHINE Aug. 25, 1953 Filed marchze, 1947 4 Sheets-Sheet 1 INVENTOR. JHSPETR KIEVI T M WW Fl TTDR ways Aug. 25, 1953 Filed March 29, 1947 J. KlEVlT AUTOMATIC WEB REWINDING MACHINE 4 Sheets-Sheet 2 J'FISPER KIEVIT HTTORNEYS Aug. 25, 1953 J. KIEYIT 2,650,038

AUTOMATIC WEB REWINDING MACHINE Filed March 29, 1947 r V 4 Sheets-Sheet I 43 v 44 B031 E- h. 48 49 ,1

zzvmvrm H PER KIEYIT nrroamsvls Aug. 25, 1953 j .1. KlEVlT .AUTOMATIC WEB REWINDING MACHINE 4 Sheets-Sheet 4 IN V EN TOR.

w w V m m K m m w W R m Y Patented Aug. 25, 1953 AUTOMATIC WEB REWINDING-MACHINE- Jasper Kievit, Middletown, Ohio, assignorto-The Crystal Waxing Company, Middletown, Ohio,

a corporation of Ohio ApplicationMarch 29, 1947, Serial No, 738,037

4 Claims.

The invention relates to machines for rewinding measured lengths of web material such. as wax paper to provide rolls of lineally measured quantity for insertion into dispensing cartons. The cartons are sold for use in the home and otherwise where sheets of wax paper are withdrawn, torn 01f and used for various purposes.

In' such a machine it is my object to greatly simplify the. mechanism required for accomplishing the rewinding of a predetermined length of web; material in a roll over that now required for: accomplishing this purpose, and at the same time to speed up the interval of individual roll rewinding operations so that the hourly output of rewound rolls will be greatly increased.

The invention contemplates the elimination of a central core member for the rewound roll and employs single mandrels or spindles mounted on a turret, with such interconnecting mechanismas is required for causing the rewind spindles to go throughthe successive stages of rewind and delivery during continuous movement of the turret and with no interval of pause during the continuous operation.

The invention further contemplates a fly knife cut off operation independent of any reciproeating grooved roller within the grooves of which the knife must seat. It further substitutes a semicircular guard and guide for confining the web to a predetermined axis of rewinding operation at the start of the rewinding operation: without the necessity of enclosing that part of the machine in which the rewinding takes place as by a cage completely enclosing the rewound roll about its entire periphery. This greatly increases the speed of operation by eliminating much equipment found necessary in previous machines for accomplishing this same purpose.

The invention contemplates. rewinding a roll.

on a spindle while the spindle is itself moving from receiving to delivering position so that there is no pause in the paper feed during rewinding and another spindle is always in position to receive the web when the wound roll on anotherspindle is. in take off position.

The foregoing objects and other objects in economy of machine. construction and operation as will be later described, I accomplish by that certain combination and arrangement of parts, of which I have illustrated a preferred embodiment.

In the drawings:

Figure 1 is a side elevation of a machine incorporating my invention.

Figure 1a is a detail perspective view of the cam whichcauses the mandrel expander bars to function.

Figure 2- a plan view of the machine shown inside elevation in Fi ure 1.

Figure 3- is a detail sectional elevation showingthe rewind, and cut-off mechanism aswould appear along the line 3'-3- in Figure 2.

Figure 4- is a detail side elevation showing diagrammatically the fly knife in web severing position,

Figure 5' is a detail side elevation showing diagrammatically the fly knife in its position removed from its brief cutting off stroke.

Figure 6' is a detail perspective view of the rewind guiding mechanism.

Figure 7 is a plan view of one of the rewinding spindles.

Figure 8 is a. sectional view along the lines 8-8 of Figure 7.

Figure 9 is a cross sectional View of a rewind spindle as would appear along the lines 9-.9 in FigureB.

Figure l0-is a cross sectional view showing the spindle expander bars in retracted position.

Figure 11 is a front elevation of a friction device which I may employ.

The. web-feeding mechanism Referring firstto Figures 1 and 2, the supply roll of paper is indicated at I. The web 2 from the supply roll feeds. up over a roller 3 and then down between thedriven roll 4 and a spring tensionedrubber covered upper roll 5. The frame members of the machine are indicated at 6. A motor 1 having a pulley 8 and. belts 8a drives a pulley 9- mounted on the shaft I!) to which the driven roll 4 is keyed.

The shaft II on which the upper roll 5' is mounted is journaled" in sliding blocks l-Z tensioned downwardly by adjustable spring 13'.

The rolls 4 and 5. may conveniently be one foot in circumference so that every revolution of the shaft [0 causes one foot of paper to be fed between the rolls 4 and 5. The upper shaft H and roll 5 is driven by spur gears M, Ma on the shafts HI and II.

The rewindz'ng mechanism Theshaft lllhas a gear l5 and chain [6 which drives a gear ll on a speed reduction unit l8. A sprocket l9, rotating at reduced speed due to gear reduction in the speed reduction unit, has a chain 20 which drives a sprocket 2| on the arbor shaft .2 2.

The turret mechanism The arbor shaft has rotatably mounted on it a sprocket 23 which is fixed on the hub of a sleeve 24 which rotates on a horizontal axis and which carries a bull gear 25 which meshes with driven gears 26 and 21, the former rotatably journaled' on one of the spindle or mandrel shafts'28 and the latter on the other spindle shaft 29. Both spindle shafts 28 and 29 are journaled in ball bearings in the turret 30 which is-fixed on the shaft 22.

It will be observed; that the gear reduction (for example if 100 foot rolls of paper are being rewound) is such that for every 100 revolutions of the shafts ii], I the arbor shaft 22 makes onehalf revolution.

However, the spindle shafts 28 and 29 must be rotated rapidly to enable each spindle during one-half revolution of the turret to rewind the 100 ft. web of paper. The sprocket 23 therefore is connected by a chain 3| to a large sprocket 32 fixed on the shaft The gears 26 and 21 carry the driving friction clutch elements 33, 34. The friction clutch elements 33, 34 drive the driven clutch elements 35, 36, which are respectively fixed on the spindle shafts 28 and 29. The only time the shafts 28, 29 are not in rotation is when a braking mechanism, to be described, causes the clutches to slip.

The cam wheel and fly knife operation The shaft 22 extends across the machine and carries a sprocket 3'! which carries a chain 38 which drives a sprocket 39 on a shaft 40. The shaft 40 carries the cam wheel 4|. The cam wheel has an abrupt step off track or indentation 42 which actuates the fly knife shaft.

The fly knife shaft 43 has an arm 44 fixed on it which has pivoted thereto a member 44a carrying a roller 45 held against the outer periphery of the cam wheel 4| by a spring 46 fixed to a post 47 mounted on the machine frame. The shaft 43 carries two knife supporting bracket arms 48. The arms 48 carry a series of rollers 49 and a knife 56.

In the operation of my machine I have found that the large cam 4| does not rotate smoothly under all requirements. To correct this condition I may employ a friction wheel mounted on the cam shaft 43. As illustrated in Fig. 11 the wheel 15 is fixed to shaft 46 by any convenient means such as the set screw 16. The periphery of the wheel is engaged by a pair of friction members I1 which are pivotally mounted upon a stand 18 fixed in the frame of the machine. At their upper ends the members 11 are perforated as at 19 to receive a bolt 80. A compression spring 8| abuts the head of the bolt and one of the members Tl as shown, to urge the members TI together so that friction will be created tending to retard rotation of the shaft 40 and its cam 4|. be noted, is adjustable and results in smooth rotation of the cam.

The guide mechanism On the side of the machine removed from the cam wheel 4| the shaft 43 has a collar formed with a short link arm 52 extending from it. A link 53, which is connected to the arm 52 as best seen in Figure 1, is adjustable by means of a turnbuckle thread and has a yoke 54 which is pivotally connected with the short arm 55 of the lever 55-56, see also Figure 1. The long arm 56 of the lever 55-56 carries the guiding mechanism which is best shown in Fig. 6 and which will This frictional loading of the shaft, as will winding operation to a proper axis of rotation.

The cut-017 and rewind operation The cutting off operation and the start of a new rewinding operation is best illustrated in the diagrammatic Figures 4 and 5. Figure 5 shows the normal position of the parts, the spindle 29 having wrapped about its periphery a measured length of rolled Web (for convenience let us say 100 ft.). The rolled web is ready to be removed by an operator for packaging. The spindle 2B is shown with the web starting to be rewound on it.

In Figure 4 that interval is diagrammatically shown when the web has been severed and the cutting knife 56 is tucking the oncoming cut edge of the web, coming from the supply roll, into the space between the curved guide fingers 51a and the outer peripheral surface of the spindle 28.

The guiding mechanism, in addition to the series of spaced U-shaped guide fingers, carries a series of rotatable rollers 58 mounted on shafts 59. The spacing of the rollers 58 on one shaft 59 from the rollers 58 on the other shaft 59 is such that slight clearance is provided from the surface of the spindle so that the tucked in edge of the advancing web is smoothly wound about the spindle 28. After several windings have been made the roller 45 runs out of the detent and the parts resume their normal position as shown in Figure 5 to be actuated again at the completion of another cycle when the spindle 29 from which the measured r011 has been removed comes into position for the start of another rewinding operation.

Since the circumference of the feed rolls 4 and 5 is one foot, one hundred revolutions will feed one hundred feet of web. The speed reduction mechanism, causing the shaft 22 to rotate, is such that this shaft carrying the turret 36 rotates half a revolution for one hundred revolutions of the rollers 4 and 5. The sprocket 31, chain 38 and sprocket 39 during this one-half revolution of the turret causes the shaft 40 and. cam wheel 4| to make one complete revolution so that there is one fly knife and guide mechanism operation each time a spindle 28 or 29 has moved from the start of the rewind position to the discharge position and the web is severed and a new roll started.

The bull gear 25 and gears 26, 21 are rotated at such speed as will cause one hundred feet of web to be rewound during one-half revolution of the turret 30.

It will be observed that the cutting off of the web and the tucking in of the cut end of the web for a subsequent rewinding operation occurs during norma1 rotation of both spindles at a peripheral speed equivalent to the normal feed of the feed rolls H], N, there being no interval of pause during this operation.

The expanding spindles The spindles on which the web is rewound are best illustrated in Figures 7 to 10. The spindle 28 is rotated by the driven clutch element 35. The driving clutch element 33 is secured to the gear 26. The spindle 28 has a cylindrical axial opening through which an expander bar operating rod 60 extends. The portion of the spindle on which the web is rewound is counterbored as shown at El and a plurality of expander bars 62 extend through slots 63 in the spindle. The bars 62 have extensions 64 at their ends which prevent the outer portions of the bars from slipping out through the slots. Each expander bar has a pair of diagonally recessed orifices 65 into which the rims 66 of conical shaped expander lugs 61, secured to the rod 60, extend.

As indicated in Figure 8, when the rod 00 moves to the right, the expander bars are drawn in so that their outer surfaces move radially inward into alignment with the outer peripheral surface of the spindle.

A coil spring 68 bearing against a fixed collar 69 on the rod 60 tensions the rod to move to the left. Set screws secure the expander lugs 67 on the rod 60. The spring tension urging the expander rod 60 to the left, as shown in Figure 8, keeps the expander bars 62 normally in expanded position as shown in Figure 9. However, it will be obvious that when the expander operating rod 60 is moved to the right, as shown in Figure 8, the expander bars will be retracted as shown in Figure 10.

To accomplish this expansion and retraction in proper cycles a cam plate II is provided having a detent 12 at the position where the rewound roll of paper is to be withdrawn from the spindle. An operator cannot conveniently withdraw a wound roll of paper with the expander bars in normally expanded position so the bars are retracted by contact of the end of the bar -60 against the cam plate, to facilitate withdrawal of the rewound roll by an operator.

Not only can the operator not remove the rewound roll with the expander bars expanded but the rotation of the spindle must be stopped at this interval. This is accomplished by a brake shoe 13 (see Figures 1 and 2). Collars 35a and 36a, which are pinned to the shafts 28 and 29 respectively, at the proper interval for withdrawing the roll, bear against the brake shoe '|3the clutch element 35 or 36 slips and the rotation of the spindle is temporarily stopped. As soon as the elements 35a, 36a ride off the brake shoe rotation begins again so that when the spindle reaches the position of the spindle 28 shown in Figure 4, it is rotating at full speed again. The speed of rotation of the spindles is so regulated by the drive from the sprocket 32 as to rewind one hundred feet of web during movement of the turret one half turn. It is to be understood that when in the claims I refer to the brake shoe bearing against the driven clutch element to effect braking of a mandrel, I intend to include those structures wherein the brake shoe bears against the driven clutch elements 35 and 36 or the collars 35a and 36a or the very shafts 28 and 29 themselves or members fixed thereto.

It will thus be obvious that I have provided an exceedingly simple mechanism in which there is no interval of pause during the continuous operation. The rotating spindles, during a half rotation of the turret, continue to rewind the web at the speed at which the web is being fed. The feature of stopping the rotation and retracting the expander bars, at the rewound roll Withdrawing position, makes the strength of the web and the possibility of its tearing the only drawback to an operating speed by which greatly increased rewinding capacity is achieved, over any other machine which requires diminution of speed at the start of the rewinding operation.

While the machine illustrated does not have an automatic take-off for the rewound roll, the

adaptation of the machine for an automatic take-off which will eliminate the need for an operator to remove the rewound rolls manually, will be well within the skill of an experienced mechanic.

Of course, by changing the gear ratio rewound rolls of greater or lesser length may be controlled.

Having thus described my invention, what I claim as new and desire to secure by Letters Patent is:

1. In a rewinding machine of the class described, a rotatable turret; means for continuously rotating said turret at a constant, relatively slow rate; two rotatable mandrels mounted on said turret at diametrically opposed points on either side of the axis of rotation of said turret; driving means for rotating said mandrels at a relatively high rate, said driving means including a drivin clutch element and a driven clutch element; each of said mandrels during one complete revolution of said turret passing through a winding cycle and an unloading cycle, said cycles beginning and ending when the turret is in a position with both said mandrels lying in the plane of the web being rewound, the winding cycle of each mandrel occupying that half of the turret revolution in which the mandrel is being moved in the direction of web movement, and the unloading cycle occupying that half of the turret revolution during which the mandrel is being moved in the direction opposite said web movement; a brake shoe bearing against the driven clutch element following completion of the winding cycle whereby to brake said mandrel; means for collapsing said mandrel following completion of the winding cycle; means for advancing the web to be rewound; means to connect said web to a mandrel at the start of a winding cycle; and means to sever the web from a mandrel at the start of an unloading cycle.

2. The machine of claim 1 in which said brake shoe is arcuate, said shoe bearing against said driven clutch element only during the unloading cycle.

3. The machine of claim 1 in which the said mandrels are each provided with a spring biased rod to maintain said mandrels in expanded condition, said collapsing means including a cam plate which contacts said rod and moves the rod against its spring only during the unloading cycle.

4. The machine of claim 1 in which the means to sever said web comprises a knife mounted on a lever, said connectin means comprising guide fingers and rollers mounted on a second lever, and a cam wheel normally maintaining said levers apart, said cam Wheel having an indentation whereby said levers are brought towards one another to sever said web between the mandrels at the start of an unloading cycle for one mandrel and to connect said web to said other mandrel at the start of its winding cycle.

JASPER KIEVIT.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 601,495 Cornell et al. Mar. 28, 1898 955,584 Denning Apr. 19, 1910 1,966,525 Schultz et al. July 17, 1934 1,976,641 Vernon et al. Oct. 9, 1934 2,200,000 Johnstone May 7, 1940 2,403,147 Westergaard July 2, 1946 

